Device for actuating double seat valves

ABSTRACT

The invention relates to a device for actuating double seat valves, which are especially suitable for the food and beverage industry and which have an independently actuated first closing element ( 3 ) and a second closing element ( 4 ) actuated dependently on it, whereby the actuation ( 100, 200 ) always shows via a main adjustment device ( 100 ) for the full open position (H) as well as, for the case of maximum requirements, the respective individual adjustment devices ( 200; 200.1, 200.2 ) which are assigned to the closing elements ( 3, 4 ) for generation of the partially open positions (T 1 , T 2 ) for the seat cleaning of the closing elements ( 3, 4 ). The object of the invention is to design a device according to this generic type, that is constructed as simply as possible and that the first partially open position (T 1 ) of the independently actuated closing element ( 3 ) is adjustable from the outside of the device. This is achieved in that a stop position of the second actuating piston ( 205 ) relative to the housing ( 201/202 ) provided for the first partially open position (T 1 ) of the first closing element ( 3 ) of the individual adjustment device ( 200 ) and is adjustable from its exterior in the area between the main adjustment device ( 100 ) and the individual adjustment devices ( 200 ) through a stop nut ( 214 ).

TECHNICAL FIELD

The invention relates to a device for actuating double seat valves,especially for the food and beverage industry, according to the preambleof claim 1.

BACKGROUND OF THE INVENTION

A device according to this generic type is known from DE 31 33 273 C2.With this device the individual adjustment devices are to be additivelyinserted between the main adjustment device and a lantern housing belowthe main adjustment device, which solely generates the full stroke forthe full open position as a stand-alone adjustment device withoutchanging the neighboring standard members. These achievable advantagesusing this so-called “modular” actuator concept consist particularly inthat to the greatest possible extent a standardized double seat valve,which has a standard actuator available for the generation of the fullopen position, through additive insertion of relatively simpleindividual adjustment devices acquires special functions, such as thegeneration of partially open positions of both closing elements. Herethe text explicitly shows that the stroke limit for both of thepartially open positions is achieved by permanent stops. In thisconnection it is further proposed to make the stroke limit using anintermediate ring which is located between the pistons causing theopening movement and the permanent stops assigned to each of them.Furthermore it is proposed, without illustrating and describing adefinite solution here, to make the necessary stoke limit using stopsaxially movable within limits from outside of the adjustment device forthe partially open positions.

With the preceding briefly defined double seat valve with permanentstops for the partially open position a disadvantage has emerged, thatthe stops are not able to be modified axially within limits. Thereforein practice the situation can arise that at the initial startup of thedouble seat valve both of the partially open positions turn out to beeither too small or too large. This result is dependent on which totaltolerance results from the sum of the individual tolerances of theparticipating members of the double seat valve for the implementation ofthe partially open positions. An insufficient partially open positionleads to an insufficient seat cleaning or no seat cleaning at all; thelatter then when the partially open position moves into the range of theelastically reshaping seat seal of the concerned closing element. Apartially open position which is too large constantly leads to anunnecessary high consumption of cleaning solution and under theseconditions the danger exists, especially on the independently actuatedclosing member, that the remaining annular gap passage after theexecution of the partially open position between the two closingelements is measured too small in order to discharge the cleaningsolution flow, which is introduced by the seat cleaning over the exposedseat surface of the independently actuated closing element from theassigned valve housing member as unpressurized as possible, as isrequired for safety reasons. In the worst case the annular ring passagedoes not even materialize and the two closing elements collide with eachother.

From the realization that the individual members cannot be so closelytoleranced that the total tolerance which inevitably results remainswithout a disadvantageous influence on the desired partially openposition, up to now as a rule the necessity arose with the previouslynamed known double seat valve to adjust the permanent stops on eachresulting actual situation. This resulted preferably in that theintermediate rings between the piston and the permanent stop were eachconstructed and installed with the exact required axial dimension. Thistype of adjustment of the actuator of the double seat valve is complexand therefore expensive, since the double seat valve must first becompletely assembled in order to establish the actual situation, andafterwards must be partially disassembled in order to install the properintermediate rings and finally again be reassembled. Modifications tothe partially open positions by differing operating conditions and/orwear of the members can only be compensated for, looked at over theservice life of the double seat valve, through repetitions at timeintervals of the previously described procedure.

The necessity arises from the last-mentioned disadvantage with a doubleseat valve of the type in discussion to make at least the criticalpartially open position, namely that of the independently actuatedclosing element, as simple to adjust as possible, preferably from theoutside. The DE 31 33 273 C2 describes no definite solutions for this;at best inadequate recommendations are found there.

In DE 31 08 973 C2 a control device for double seat valves is describedwith which the stop position of the pistons is adjustable, forgeneration of the partially open position relative to the control rod.The modification can thereby be done from outside of the individualadjustment devices using control features. But the possibility foradjustability is paid for in that both control rods are guided throughthe main adjustment device upwards and end in a control cylinder commonto both closing elements. The disadvantage of this arrangement is thatboth control rods must be designed relatively long and thereforestructurally critical since they, starting from the closing elements inthe valve housing, must penetrate or by pass the lantern housing, themain adjustment device and the individual adjustment devices. Thenecessary accessibility of the control feature of the individualadjustment device adjacent to the main adjustment device requires therean additional lantern housing, which raises the overall height of thetotal arrangement. A further disadvantage is that the arrangement of acontrol head on the end of the control device, which in the higheststage of extension monitors among other things the path of motion andthe discrete end position of the closing element and takes over theentire control logic as well as the pilot valves for the activation ofthe adjustment devices with pressurizing medium, is not possible withouteliminating the accessibility of the control features arranged there.

From EP 0 868 619 B1 a device for actuating double seat valves of thetype in discussion is known which, along with a main adjustment device,has two individual adjustment devices for the implementation of the twopartially open positions. All adjustment devices are placed in a commonactuator housing, whereby the two individual adjustment devices arelocated between the main adjustment device and a lantern housingadjacent to the valve housing. This arrangement has the advantage, justas one according to DE 31 33 273 C2, that the control rod of thedependently actuated closing element can end already in the assignedindividual adjustment device and that the control rod of theindependently actuated closing element is only guided through the mainadjustment device into the control head as needed.

In addition each of the provided stop positions of the pistons for thepartial stroke limit of the closing element relative to each control rodon it is able to be modified from the exterior of the actuator device inthe area of the lantern housing. Stop sleeves which penetrate each otherin the axial direction are provided as control features through whichthe control rods, which are located concentrically to each other, areguided through, whereby the outer stop sleeve in the actuator housingand the inner stop sleeve in the outer one are each arranged to beadjustable and fixable.

The preceding briefly described actuator is also designated in expertcircles as a so-called “integrated” actuator, because in a commonhousing it accommodates the main adjustment device for the full openingstroke H as well as the individual adjustment devices for the partiallyopen positions T1 and T2. These types of actuators are as a rulecompactly built and make it possible to arrange a so-called controlmodule and/or control head directly above the main adjustment device, ifthe individual adjustment devices are arranged in the previouslydescribed manner in reference to the main adjustment device. A furtheradvantage results from the adjustability of the partially open positionsfrom the outside, although the proposed solution in this regard is verycomplex.

The significant disadvantages of the integrated actuators also arisefrom the fact that they are designed for the maximum requirements whichare placed on double seat valves of the type under discussion. Maximumrequirements are then given if, along with the full opening stroke Hwhich is executed by the main adjustment device, the partially openpositions T1, T2 of both closing elements for the execution of therespective seat cleaning, which is carried out by an individualadjustment device assigned to each closing element, are necessary. Sincea large percentage of the double seat valves placed in installations inthe food and beverage industry are in applications without thepossibility or necessity of seat cleaning, because only mixingefficiency is required, integrated actuators in which only the mainadjustment device is activated are normally too complex and thereforeuneconomical. In practice these types of applications then fall back on“normal” actuators (standard actuators) for double seat valves, whichonly accommodate a main adjustment device for the full open position H.Thereby the quantity of integrated actuators from a manufacturer ofdouble seat valves is reduced, since each double seat valvecorresponding to the requested requirements is only equipped with asuitable actuator for this purpose and thereby results as the case maybe in uneconomical manufactured quantities for integrated actuators.

The dependently actuated closing element of the double seat valve, whichwith its two seals is also designated as a double disk, is in fact notcritical during the seat cleaning in regards to its partially openposition T2 and therefore can be moved against a permanent stop for theexecution of the assigned seat cleaning position. This stop thereforeneeds no complex pre-adjustment or readjustment. During seat cleaningthe cleaning solution is normally under pressure on the dependentlyactuated closing element, so that this must be opened by the partialstroke T2 against the resulting closing force from the correspondingpressure and the assigned operative surface of this closing element. Toovercome this closing force or holding down force the assigned secondindividual adjustment device is to be dimensioned accordingly. Either asufficiently large piston surface of the actuating piston in this secondindividual adjustment device is to be provided or the pressure of thepressurizing medium loaded on the actuating piston is to becorrespondingly increased if there are restrictions in regards to thediameter dimension of the actuating piston. An adjustment of theactuator to the existing pressure conditions using a correspondingdimensioning of the actuating piston is always primarily a question ofcost and is normally only chosen if other possibilities are notavailable. The choice of a higher pressure of the pressurizing medium isnormally preferred; however in practice it is always eliminated if theinstallation or plant in which the cleanable double seat valve isinstalled does not have available a pressure level in this regard or outof cost considerations can not be additionally done.

The object of the present invention is to design a device according tothis generic type that is constructed as simply as possible and that thepartially open position of the independently actuated closing element isadjustable from the outside of the device.

Furthermore in the scope of an advantageous embodiment of the proposeddevice, a larger flexibility should be ensured in the adjustment of thesecond individual adjustment device for the partial stroke movement ofthe dependently actuated closing element to the available pressure ofthe pressurized medium.

SUMMARY OF THE INVENTION

The object is solved by the features of claim 1. Advantageousembodiments of the proposed device are the subject matter of thesubclaims.

An important advantage of the proposed solution lies in that for thefirst time a solution is disclosed on how, with a modular actuatorconcept in which the main adjustment device has a standard actuator andthe individual adjustment devices are independently designed and areinserted between the standard actuator and the valve housing or alantern housing connected with it, the (critical) partially openposition of the independently actuated closing element is adjustablefrom the outside of the device.

For that reason henceforth it is possible to equip double seat valveswhich are capable of seat cleaning and those which are not capable ofseat cleaning with the same standard actuator for the full openingmovement of the valve. Thus on the one hand the best conditions for aneconomic quantity of production pieces of this type of standardactuators prevail and on the other hand for each double seat valve onlythe necessary corresponding actuator parts are used. In addition thecritical partially open position of the independently actuated closingelement is adjusted from the outside of the device from case to casedepending on the given total tolerance of the participating elements.The less critical partially open position of the dependently actuatedclosing element is controllable by a permanent stop, since the membersparticipating in the occurring partially open position can be tolerancedso that the added total tolerance has a subordinate influence on thenecessary partially open position.

Furthermore the proposal makes possible the implementation of specialfunctions, namely the execution of the partial stroke movement T1, T2 ofboth closing elements for the purpose of their seat cleaning by means ofstand-alone individual adjustment devices, economically justifiable forthe initial equipment of double seat valves, as well as for therefitting of already available double seat valves, which were previouslynormal switching, however capable of seat cleaning.

The insertion of stand-alone individual adjustment devices in arelatively complex structure, as is demonstrated in a double seat valve,is therefore possible because the individual members are as far as ispossible normed or standardized in their connections and joints withinthe scope of a modular system. This is true for the main adjustmentdevice (standard actuator) as well as for the lantern housing adjacentto the valve housing and the control rods passing through from the uppervalve housing member. The housing connection is preferably done usingstandardized so-called clamping ring connections and the control rodsare screwed together at the corresponding locations. Due to the locationof the individual adjustment devices between the main adjustment deviceand the valve housing, the other side of the main adjustment deviceremains free for the arrangement of a control device, which among otherthings monitors the path of motion and the discrete end locations of theclosing elements and takes over the entire control logic as well as thepilot valve.

An advantageous embodiment is designed considering an execution of thepartial stroke limit of the independently actuated first closing elementas simply as possible and accessible from the outside of the device, todetermine the stop position of the second actuating piston for the firstpartially open position T1 indirectly over a drive sleeve, which issupported and sealed on the one side in the second actuating piston andon the other side to a guide component, which engages from outside inthe third housing member of the individual adjustment devices as aseparate member and complementary supplements this. The drive sleevethereby finds its stops on the stop nut which is located on the guidecomponent and is accessible from the outside and adjustable and fixable.The location of the guide component enables this to be pulled so far outof the third housing member of the individual adjustment device untilthe stop nut is accessible. The adjustment of the stop nut is preferablydone using a threaded connection with fine threads, specifically forexample a grub screw. The access to the guide component is thus possiblein a simple manner in that the clamping ring connection between the mainadjustment device and the individual adjustment devices is detached andall of the members directly or indirectly connected with the firstactuator stem of the main adjustment device are pulled out from thethird housing member of the individual adjustment devices by thenecessary axial distance.

The preceding mentioned ability for extension of the members which comeinto question arises from a further advantageous embodiment, whichprovides for the arrangement, made up of a guide component in connectionwith the stop nut, the drive sleeve, the second actuator stem inconnection with the lock nut, a third actuator stem and a second springlocated between the latter and the second actuator stem, is able to betotally extended from the assembled individual adjustment devices in thedirection of the main adjustment device which is able to be flanged onthe latter.

In order to ensure the most delay free response of the first individualadjustment device as possible after its activation with pressurizingmedium, a further proposal allows to design the axial extension of thedrive sleeve larger than the full open position H of the double seatvalve. Through this step the second actuating piston is introduced asnear as possible to the third actuating piston, so that the volume ofthe second pressurizing medium chamber, which is formed within theindividual adjustment devices between these two actuating pistons andwhich produces the first partially open position T1, is minimized.

For easier adjustment of the actuator of the second individualadjustment device, which is designed to implement the partial stroke T2for the dependently actuated closing element, a different, however aboveall a relatively low, pressure of the pressurized medium is provided bya further embodiment of the proposed device, that the third actuatingpiston is fixed, however able to be detached, on its side facing thesecond actuating piston with a smaller diameter additional piston, thatthe additional piston working together with a housing ring fixed on thehousing of the individual adjustment devices forms a fourth pressurizingmedium chamber, which is connected with a third pressurizing mediumchamber formed between the third actuating piston and the fourth housingmember, and that with the introduction of a third pressurizing mediumflow to the third pressurizing medium chamber also an additional forceresults affecting the additional piston additionally in the fourthpressurizing medium chamber, which superimposes itself additively on theforce affecting the third actuating piston. Through the arrangement ofan additional piston on the actuating piston of the second individualadjustment device the latter gains a function, which is also oftendesignated as a so-called “batch function”. The actuating pistonexperiences quasi a surface enlargement through the additional piston,which indeed does not have the effect of a larger diameter pistonsurface by the chosen arrangement, but rather is found in a second,parallel plane. In the present case the pressurizing medium reaches theactuating piston first and afterwards the additional piston, in order todevelop each time a force on the respectively arranged pistons throughthe installed piston surfaces, whereby these two forces, the force onthe actuator pistons and the additional force on the additional pistons,are additively superimposed on each other.

A compact arrangement of the second individual adjustment device withadditional pistons is attained according to a further proposal, in thatthe additional piston has a larger diameter external piston section anda smaller diameter interior piston section, that the interior pistonsection is sealed on the face side against the third actuating pistonand screwed to it, that the exterior piston section is sealed on thecircumference against the shell of a cylindrical cutout in the housingring and the interior piston section is sealed on the circumference in acoaxial through-bore in the housing ring, and that in the connectionarea of the third actuating piston with the additional piston arelocated in the former a first pressurizing medium channel and in thelatter a second pressurizing medium channel, which correspond with oneanother and connect the third pressurizing medium chamber and the fourthpressurizing medium chamber with one another permeable to thepressurizing medium. The housing ring which is fixed in the housing ofthe individual adjustment devices forms on the one hand, with theadditional pistons, the necessary additional fourth pressurizing mediumchamber and creates on the other hand, through its housing side support,the physical conditions for the adding of the additional force to theforce on the third actuating piston. The latter, in connection with thefourth housing member, borders the third pressurizing medium chamber, inwhich the third pressurizing medium flow is first introduced in order tothen finally reach into the fourth pressurizing medium chamber.

According to a further advantageous embodiment the housing ring has aradial projection on the circumferential side, with which the housingring is located form fit to the connection area between the third andthe fourth housing member. The assembly of the housing ring is simpleunder these conditions, since the latter is inserted in the third andthe fourth housing member, before these are then integrally joined withone another.

The device according to the invention is designed either with or withoutadditional pistons. Since it is an advantage for the housing of theindividual adjustment devices with the pressurizing medium connectionwhich comes into question to always be designed identically regardlessof whether an additional piston is present or not, a further embodimentof the proposed device is designed in that a second pressurizing mediumconnection for a second pressurizing medium flow for pressurization ofthe second actuating piston which is located in the third housing memberdischarges into a preceding second pressurizing medium chamber in thearea between the third actuating piston and the housing ring, and thatthe preceding second pressurizing medium chamber is connected with asecond pressurizing medium chamber designed between the second actuatingpiston on the one hand and the housing ring in connection with theadditional piston on the other hand, through at least one connectionchannel, which is located in a cylindrical cutout on the outerperipheral member of the housing ring. Through this arrangement thesecond pressurizing medium connection can remain at any position in thehousing of the individual adjustment devices on which it is located ifthe second individual adjustment device is not equipped with anadditional piston. The connection channel in the housing ring ensurespermeability for the pressurizing medium, so that the pressurizingmedium introduced through the second pressurizing medium connection canget from one side of the housing ring to its other side below the secondactuating piston.

The relatively simply designed total actuating system, whichadditionally experiences a clear functional separation by its modulardesign, is also relatively unproblematic in regards to a summation ofadded process tolerances of its individual members, so far as it effectsthe ones which are responsible for the second partially open position T2of the dependently actuated second closing element. This results fromthe fact that the second closing element in its seat cleaning positionopens each time uncritically in the assigned second valve housing memberand therefore a danger of collision in the process of the secondpartially open position T2 does not exist. For this reason the proposeddevice in this regard is does not require adjustable stops for thelimiting of the partial stroke movement of the second closing element inthe process of its seat cleaning, rather it is the most simpleimaginable end-of-travel limit possible. In this regard the proposalprovides that the end-of-travel limit of the third actuating piston forthe second partially open position T2 is determined by a stop ring orhousing ring permanently located on the housing and axially moveablethrough the third actuating piston.

In order to fully utilize the advantages of the modular actuatorconcept, i.e. to be able to use the main adjustment device (as standardactuator alone) and the individual adjustment devices as flexibly aspossible, a further proposal allows to design the control rod guidedthrough from the first closing element up through the main adjustmentdevice in several parts, namely in three parts. Here it is provided thatthe first control rod is screwed using its external threads with asecond actuator stem in the area of a second individual adjustmentdevice, that the second actuator stem is also screwed using its externalthreads with a first actuator stem of the main adjustment device in thearea of a first individual adjustment device, and that the screwconnection of the actuator stem is securely screwed using a lock nutlocated on the external threads of the second actuator stem. Thisarrangement allows the first control rod to also be connected directlywith the first actuator stem, if the double seat valve is only to beequipped with a standard actuator. The jam nut prevents that the torquetransmitted through the compression of a main spring in the mainadjustment device onto the first and the second actuator stem or thefirst actuator stem and the first control rod loosens the screwconnection in question between the respective pairing.

The loosening of the screw connection between the first control rod andthe second actuator stem is thus prevented according to a proposal thatin the internal threads of the second actuator stem a threaded insert(for example a so-called HeliCoil insert) is provided which works as ascrew lock.

The continuous pressurizing medium bore hole in the longitudinal axis ofthe first actuator stem is advantageously used as a route of transportfor the pressurizing medium to the first pressurizing medium chamber,whereby the distribution of the pressurizing medium in this space isdone using the respective cross holes.

The housing of the main adjustment and each of the individual adjustmentdevices can be easily designed with the same diameter since both thefull open position H, as well as the first partially open position T1,is directed against the same pretension force of the main spring in themain adjustment device. Thereby it is again possible, as a furtherproposal provides, to make the housing members of the main adjustmentdevice and those of the individual adjustment devices from housing roughparts of the same shape, whereby a further cost reduction results.

The manufacturing costs can be further reduced in that the housingmembers of the main adjustment device and those of the individualadjustment device are each integrally joined together, preferablythrough welding.

In order to reduce costs as well as weight in the proposed device, it isfurther provided for that the actuating piston of the individualadjustment devices and each of the main adjustment devices are all madeof corrosion resistant light alloy, preferably from salt-water proofaluminum.

When disassembling components which are under spring pretension, thereis a fundamental safety risk. In order to minimize this safety risk, afurther proposal provides that after loosening of the screw connectionbetween the first control rod and the second actuator stem, thepretensioning of the second spring is relieved, which is effectivebetween the second and the third actuator stem.

BRIEF DESCRIPTION OF THE DRAWINGS

Exemplary embodiments of the proposed device for actuating double seatvalves according to the invention are represented in the drawing and aredescribed following according to design and function, wherein:

FIG. 1 shows a middle cross-section through a first embodiment of adevice for actuating double seat valves of the generic type according tothe invention, whereby the referenced double seat valve in the closedposition in this reference is located below the proposed device and acontrol device (in broken-out section) is located above it.

FIG. 2 shows a middle cross-section through the device according to FIG.1, whereby the illustrated device represents the position of themovement dependent members so that these correspond to the closedposition of the two closing elements which are represented in the lowerarea of the illustration in sections.

FIG. 3 also shows a device in middle cross-section and both assignedclosing elements according to FIG. 2, whereby the members of the devicecoming into question henceforth are found in one of the correspondinglocations of the full open positions of the two closing elements;

FIG. 4 also shows in middle cross-section the device and both assignedclosing elements according to FIG. 2, whereby the parts of the devicecoming into question henceforth are found in one of the correspondinglocations of the seat cleaning positions of the independently actuatedfirst closing element;

FIG. 5 also shows in middle cross-section the device and both assignedclosing elements according to FIG. 2, whereby the parts of the devicecoming into question henceforth are found in one of the correspondinglocations of the seat cleaning positions of the dependently actuatedsecond closing element;

FIG. 6 a middle cross-section through a second embodiment of theindividual adjustment devices according to the invention, whereby thethird actuating piston is connected with an additional piston and thusthe assigned second individual adjustment device supports a so-called“batch function” and

FIG. 6 a a section from the individual adjustment devices according toFIG. 6 in the area of the screw connection between the third actuatingpiston and the additional piston.

DETAILED DESCRIPTION

The proposed device 100, 200 (FIG. 1) is used for actuating a doubleseat valve, that is essentially made up of a valve housing 1 with afirst and a second valve housing member 1 a or 1 b, respectively, twoclosing elements 3 and 4 which are designed as seat discs and moveindependently to each other using the assigned adjustment rods 3 a or 4a, respectively, in each case, a seat ring 2 which makes a connectionbetween the valve housing members 1 a, 1 b using its inner connectionorifice 2 c, a lantern housing 6 connecting the second valve housingmember 1 b with the device 100, 200, as well as a control device 7,whereby the latter is arranged on the side of the device 100, 200opposite to the double seat valve.

The independently actuated first closing element 3 is equipped with afirst seat seal 8 working in the radial as well as in the axialdirection, which is assigned a first seat surface 2 a (FIG. 2), which isformed from a part on the end side and adjacent to the first valvehousing member 1 a which borders the connection orifice 2 c in the seatring 2. The dependently actuated second closing element 4 also has inits seat area a second seat seal 9 which works in both the radial andaxial direction, and which works together with a second seat surface 2b, which is designed on the other end of the seat ring 2. Between thetwo closing elements 3, 4 a leakage chamber 5 is formed which, in thefull open position H of the double seat valve (FIG. 3), is sealedagainst its environment by means of a seal 10 working exclusively in theaxial direction, which is arranged on the end surface of the secondclosing element 4 facing the leakage chamber 5.

The leakage chamber 5, as well as the adjacent parts impinged by theflow, can be cleaned in the closed, as well as in the open, position ofthe double seat valve (see also FIGS. 2, 3 along with FIG. 1) by meansof a cleaning solution R which is introduced through a cleaning solutionconnection 11 which is located in the area of the lantern housing 6 onthe second control rod 4 a, preferably a non-specified ring channel,between the first and the second control rods 3 a, 4 a. The removal ofthis type of “externally” introduced cleaning solution R from theleakage chamber 5 is done here by a non-specified connection line whichis arranged in a tubular extension leading through the first valvehousing part 1 a and out of it on the first closing element 3.

The removal of an “internally” introduced cleaning solution by theparticular seat cleaning stream R1, R2 from the internal chamber 5,which is introduced from the valve housing part 1 a or 1 b assigned atany one time during the seat cleaning of the first or the second closingelement 3, 4 (also see for this FIGS. 4 and 5), is done in the samemanner as with the external cleaning introduction R. In the seatcleaning of the first closing element 3 this is pushed so far in thedirection of the second closing element 4 (FIG. 4), that a firstpartially open position T1 consequently occurs, in which the first seatseal 8 has left the assigned first seat surface 2 a gapwise and a firstseat cleaning stream R1 from the first valve housing member 1 a isgenerated over the exposed first seat surface 2 a in the leakage chamber5.

For seat cleaning of the second closing element 4 this is pushed so farin the direction of the second valve housing member 1 b (FIG. 5), thatin a thus partially open position T2 taken from the second closingelement 4, the second seat seal 9 left the assigned second seat surface2 b and a second seat cleaning stream R2 from the second valve housingmember 1 b arrived into the leakage chamber 5 on the way over theexposed seat surface 2 b.

To limit the amount of cleaning solution in each of the seat cleaningstreams R1, R2 during the process of seat cleaning, known cylindricalprojections (not illustrated) are provided on the closing elements 3, 4if necessary, oriented toward the leakage chamber 5, whereby duringgapwise removal of the closing elements 3, 4 from their assigned seatsurfaces 2 a, 2 b the second closing element 4 with its cylindricalprojection still reaches sufficiently far with radial clearance into theconnection orifice 2 c and the first closing element 3 with itscylindrical projection is always provided with radial clearance in theconnection orifice 2 c and both closing elements 3, 4 in each case forma so-called choking annular gap there with their cylindricalprojections. Alternatively the limit of the seat cleaning streams R1, R2thus are also reached in that the particular partially open position T1,T2 is not stationary generated, but rather oscillating.

To put into effect the preceding briefly illustrated switch movement ofthe closing elements 3, 4 (full opening stroke H, partially openpositions T1 and T2) henceforth the double seat valve is equipped withthe device 100, 200 according to the invention, which has the mainadjustment device 100 for the opening and closing of the double seatvalve within the scope of the full opening stroke H (FIG. 1) and theindividual adjustment devices 200 for the generation of the partiallyopen positions T1, T2. The main adjustment device 100 corresponds in itsdesign to a so-called standard actuator, with which a double seat valveof the type in question can be opened and closed on its own; Specialfunctions, such as seat cleaning, cannot be done with this standardactuator. The main adjustment device 100 is designed in a manner inregards to its peripheral housing connections and other necessaryconnections, so that when eliminating the individual adjustment devices200 it can be directly connected with a lantern housing 6, which is infact adjusted in length but is otherwise not modified. The end (externalthreads) of the first control rod 3 a is in this regard designed in sucha way, that it is complementary to an end section (internal threads) ofa second actuator stem 203 of the individual adjustment device 200, aswell as complementary to an end section (internal threads) of a firstactuator stem 103 of the main adjustment device 100, which if necessaryit is screwed with in each case. The second control rod 4 a, continueson above the cleaning solution connection 11 in a third actuator stem204 designed as a hollow rod and ends in the individual adjustmentdevices 200.

Because the position of the first closing element 3 must, if necessary,be recorded at each point in time, a position indicator rod 7 a isprovided, which is screwed with the first actuator stem 103 and ends inthe control device 7. For the control of the main adjustment device 100a first pressurizing medium connection 7 b is provided on the controldevice 7 through which a first pressurizing medium flow D1 is charged ordischarged. The latter arrives en route through a pressurizing mediumbore hole 103 a located in the first actuator stem 103 into the mainadjustment device 100. To generate the partially open positions T1, T2the individual adjustment devices 200 have a second and a thirdpressurizing medium connection 208, 209 available for the second andthird pressurizing medium flow D2, D3. A fourth pressurizing mediumconnection 210 is closed by means of a non-specified sealing plug andremains without a function in the proposed device.

The housing of the main adjustment device 100 (FIG. 2; the multiplicityof seals of the device are not specified individually here and infurther figures) consists of a first and a second housing member 101,102, which are essentially made from housing rough parts of the sameshape. A first actuating piston 104 with piston seal is located on thefirst actuator stem 103 and fixed there with a non-specified nut. Apretensioned main spring 105 finds its abutment on the one end on thefirst actuating piston 104 and on the other end on the first housingmember 101. After the installation of the first actuating piston 104,the first actuator stem 103 and the main spring 105 in both housingmembers 101, 102, the latter are preferentially integrally joinedtogether, preferably by welding. The seals and guide bushings in housing101/102 of the main adjustment device 100 are also exchangeable aftertheir final assembly. The pressurizing medium bore hole 103 a located inthe first actuator stem 103 and concentric to it is used for thetransport of the first pressurizing medium flow D1, which arrives in thefirst pressurizing medium chamber 100 a formed between the firstactuating piston 104 and the second housing member 102 through the crosshole 103 b.

Below the main adjustment device 100 the individual adjustment devices200 are additively inserted. The latter, seen from top to bottom, aremade up of a first individual adjustment device 200.1 for generation ofthe first partially open position T1 of the first closing element 3 andby a second individual adjustment device 200.2 for generation of thesecond partially open position T2 of the second closing element 4. Thehousings of the individual adjustment devices 200 are formed from athird and a fourth housing member 201, 202, which are made essentiallyfrom housing rough parts of the same shape, and after the assembly ofthe mounting parts are preferentially integrally joined together,preferably by welding.

In the third housing member 201 of the first individual adjustmentdevice 200.1 a peripheral second actuating piston 205 which is providedwith a piston seal is located, and below the second actuating piston 205in the fourth housing member 202 of the second individual adjustmentdevice 200.2 a peripheral third actuating piston 206 which is providedwith a piston seal is designed. The latter is supported moveable in theaxial direction inside on the third actuator stem 204 which is designedas a hollow rod and is able to be brought with this in the direction ofthe second partially open position T2 on a shaped recess 204 a, formedon the end of the actuator stem 204 in a clamped connection. The secondactuating piston 205 penetrates inside through a drive sleeve 212, whichhas on its end facing the third actuating piston 206 a second recess 212a on the inside and on the outside, an axial distance removed from thelatter, a third recess 212 b. If necessary the drive sleeve 212 isbrought in a clamped connection with the second actuator stem 203 usingthe second recess 212 a, which is expanded in this area in a largerdiameter headpiece 203 a. The third recess 212 b corresponds with asecond clamping flat 205 a on the second actuating piston 205, so thatthe latter using a sliding movement carried out in the direction of thefirst partially open position T1 takes the drive sleeve 212 with it inthis direction.

The drive sleeve 212 is supported and sealed on the inside on its endaway from the second actuating piston 205 on a guide component 215,which engages from the outside into the third housing member 201,supplements it complementary and is concentrically penetrated inside bythe first actuator stem 103. In the area penetrated with the thirdhousing member 201 the guide component 215 is provided with a threadedportion 215 a on the outside, on which is screwed a stop nut 214. Thelatter has on its circumference at least one cutout 214 b, with whosehelp a rotation and therefore axial movement is easily carried out. Inaddition it is ensured through suitable, not individually specified,steps that the stop nut 214 is immovably fastened in a specific positionon the guide component 215 (for example by grub screws). One of thefront faces of the stop nut 214 facing the drive sleeve 212 is designedas a fourth stop face 214 a, which corresponds with an assigned endsurface of the drive sleeve 212, designed as the third stop face 212 c.The fourth stop face 214 a forms the adjustable stop from outside of theindividual adjustment device 200 for the limit of the first partiallyopen position T1 of the first closing element 3.

The access to the stop nut 214 is done in that the clamping ringconnection between the main adjustment device 100 and the individualadjustment devices 200 is loosened and the main adjustment device 100 isremoved a small distance axially from the individual adjustment device.With this the headpiece 203 a comes to rest on the guide component 215,so that with further movements the stop nut 214 leaves the third housingmember 201 toward the outside and therefore is accessible from theoutside for the purpose of its axial adjustment. Other then theloosening of the existing clamping ring connection this procedurerequires no further disassembly of the device, since all the membersconnected directly or indirectly with the first actuator stem 103 areall extensible from the assembled individual adjustment device 200 inthe direction of the main adjustment device 100 flanged to the latter.

The second actuator stem 203 is screwed using an external screw threadwith its end facing the main adjustment device 100 and connecting to theexpanded headpiece 203 a in the area of the first individual adjustmentdevice 200.1 with the first actuator stem 103, whereby this screwedconnection is secured by a lock nut 211 located on the external screwthread. In doing so the lock nut 211 comes to rest on the one side at asecond stop face 203 b of the headpiece 203 a and on the other side atan end surface of the first actuator stem 103 designed as a first stopface 103 c.

A second pressurizing medium chamber 200 a, which is connected with thesecond pressurizing medium connection 208, is circumferentiallyencompassed by the housing 201/202 of the individual adjustment devices200, on one end face by the second actuating piston 205 and on the otherend face by the third actuating piston 206. A third pressurizing mediumchamber 200 b is formed between the third actuating piston 206 and thefourth housing member 202, which is connected with the thirdpressurizing medium connection 209.

A second spring 207 is located between the headpiece 203 a and the thirdactuator stem 204 in the area of the second individual adjustment device200.2 within an expansion of the third actuator stem 204 having a hollowrod shaped design, whose pretensioning is measured so that the secondclosing member 4 is pressed in its closing position with sufficientforce on the assigned second seat surface 2 b. In the open position ofthe double seat valve (FIG. 3) the somewhat reduced pretensioning isstill sufficient in any case, because of an insignificant elongation ofthe second spring 207, to press the closing elements 3, 4 together withsufficient force so that the leakage chamber 5 is securely sealed fromthe surroundings by the seal 10.

The end-of-travel limit of the third actuating piston 206 for the secondpartially open position T2 is done by a stop ring 213 axially movable onboth sides, which is permanently arranged on housings 201/202 betweenthe actuating pistons 205, 206 (cf. also FIG. 5). The possible traveldistance of the third actuating piston 206 to its stop on the stop ring213 is determined on the exterior by the second partial piston travel b,whereas the third actuating piston 206 can travel in the interior by athird partial piston travel c, which is designed inevitably smaller thanthe second partial piston travel b, until the third actuating piston 206ends in the clamping connection with the recess 204 a, by means of itsthird clamping flat 206 a. As a result, through the actuation of thethird actuating piston 206, a second partially open position T2 results,which is determined (T2=b−c) by the difference [b−c].

The first partially open position T1 results unavoidably from the axialdistance between the drive sleeve 212 and the stop nut 214, which inFIG. 2 is marked as the first partial piston travel a, if the headpiece203 a is located in one of the closed positions of the first closingelement 3 corresponding locations and using a first clamping flat 203 cthus has pushed the drive sleeve 212 over its second recess 212 a in anadequate axial position (first partial piston travel a; T1=a). Thesecond actuating piston 205 thereby is likewise correspondingly pushedunavoidably over the third recess 212 b of the drive sleeve 212, wherebyin this end position it is still an axial safety distance removed, afourth partial piston travel d, from the stop ring 213. As a rule thesecond actuating piston 205 would not rest on the stop ring 213, sinceit is not pressurized from the space between the second actuating piston205 and the third housing member 201. If however a displacement happensin this regard, then it is ensured in any case that the second actuatingpiston 205 is lodged on the drive sleeve 212 and remains sealed.

The double seat valve is transported in its full open position H (FIG.3), if the first pressurizing medium flow D1 of the main adjustmentdevice 100 is introduced through the pressurizing medium bore hole 103a, reaches into the first pressurizing medium chamber 100 a through thecross hole 103 b and there pressurizes the first actuating piston. Theactuating piston 104 pressurized in this manner engages with its openingforce, which comes from the pressure in the first pressurizing mediumchamber 100 a and the provided effective piston surface, directly on thefirst actuator stem 103 and consequently overcomes the pretensioningforce of the main spring 105 and if necessary the aggressive pressureand/or friction forces against the opening movement on both closingelements 3, 4. The latter are additionally to be overcome, since thefirst actuator stem 103 is connected on the one hand directly with thesecond actuator stem 203 and this in turn with the first control rod 3 aand on the other hand indirectly with the third actuator stem 204 andthis in turn with the second control rod 4 a. The full open position Hfinds its end-of-travel limit either through the arrangement of the locknut 211 on a fifth stop face 215 b inside on the guide component 215 orthrough the arrangement of the headpiece 203 a on a sixth stop face 215c outside on the guide component 215.

The seat cleaning of the first closing element 3 (FIG. 4) is donethrough the introduction of the second pressurizing medium flow D2 inthe second pressurizing medium chamber 200 a of the first individualadjustment device 200.1 en route over the second pressurizing mediumconnection 208. Thus the pressurized second actuating piston 205 ispushed in the opening direction of the double seat valve and thusadvances using its second clamping flat 205 a the drive sleeve 212 overits third recess 212 b likewise in the same direction. The drive sleeve212 comes to rest using its third stop face 212 c on the fourth stopface 214 a, of the stop nut 214. Simultaneously the second recess 212 aengages the headpiece 203 a on the first clamping flat 203 c on theinside of the drive sleeve 212, so that the second actuator stem 203,and with it the first control rod 3 a with the first closing element 3,is pushed in the partially open position T1=a. Thus the assigned firstseat surface 2 a is gapwise exposed and the first seat cleaning streamR1 reaches out of the first valve housing member 1 a en route using thegapwise opened first seat surface 2 a into the leakage chamber 5.

The seat cleaning of the second closing element 4 (FIG. 5) is completedin that the third pressurizing medium flow D3 is introduced by the thirdpressurizing medium connection 209 into the third pressurizing mediumchamber 200 b of the second individual adjustment device 200.2. Thus thepressurized third actuating piston 206 moves in the direction toward thestop ring 213 and until it gets to its stop there has to overcome thesecond partial piston travel b (cf. FIG. 2). Beforehand it gets in aclamping connection after the third partial piston travel c via itsthird clamping flat 206 a on recess 204 a so that, after a stop on thestop ring 213 from the third actuator stem 204 in connection with thesecond control rod 4 a and thus from the second closing element 4, therequired partially open position T2=b−c is completed against thepretension force of the second spring 207. The latter finds an abutmenton the headpiece 203 a, which via the second actuator stem 203 inconnection with the first actuator stem 103 and this in turn inconnection with the first actuating piston 104 is fixed securely in thisend position by the pretension force of the main spring 105. The secondclosing element 4 is removed gapwise from its assigned second seatsurface 2 b through the second partially open position T2, so that thesecond seat cleaning stream R2 from the second valve housing member 1 breaches over the gap between the exposed second seat surface 2 b and thesecond seat seal 9 into the leakage chamber 5.

In the second individual adjustment device 200.2 inside the individualadjustment devices 200 (FIG. 6), in which the third actuating piston 206with a so-called “batch function” is provided, the latter is connectedtightly, however able to be loosened, on its side facing the secondactuating piston 205 with a smaller diameter additional piston 206.1.The additional piston 206.1 working together with a housing ring 213.1fixed on the housing 201/202 of the individual adjustment device 200forms a fourth pressurizing medium chamber 200 c, which is connectedwith a third pressurizing medium chamber 200 b formed between the thirdactuating piston 206 and a non-specified bottom member of the fourthhousing member 202. At the same time the additional piston 206.1 has alarger diameter exterior piston section 206.1 a and a smaller diameterinterior piston section 206.1 b, whereby the exterior piston section206.1 a features an external diameter D_(a) and the interior pistonsection 206.1 b an internal diameter D_(i) (FIG. 6 a). The interiorpiston section 206.1 b is sealed on its frontal end by means of seals218 which are coaxially arranged with each other against the thirdactuating piston 206 and screwed with this using several of screwedconnections 206.2 distributed over its circumference. The exteriorpiston section 206.1 a is peripherally sealed against the shell of acylindrical recess 213.1 a in the housing ring 213.1 by means of a firstpiston seal 216. In the same manner the interior piston section 206.1 bis sealed peripherally in a coaxial through bore 213.1 b in the housingring 213.1 by means of a second piston seal 217. The third pressurizingmedium flow D3 is introduced over the third pressurizing mediumconnection 209 first to the third pressurizing medium chamber 200 b.From there the pressurizing medium reaches over a first pressurizingmedium channel 200 b running between the two seals 218 in an axialdirection through the third actuating piston 206, in order to finallyreach into a second pressurizing medium channel 206.1 d which is runningcorresponding with these in the additional piston 206.1 up to the fourthpressurizing medium chamber 200 c.

The housing ring 213.1 has a radial projection 213.1 con its periphery,with which it is positively fastened in the connection area between thethird and the fourth housing member 201, 202. Between the housing ring213.1 and the third actuating piston 206 a preceding second pressurizingmedium chamber 200 a* is designed, in which the second pressurizingmedium connection 208 discharges. The second pressurizing medium flow D2is introduced or discharged through the latter-for the execution of thepartial stroke movement T1 for the independently actuated closingelement 3. The preceding second pressurizing medium chamber 200 a* isconnected through at least one connection channel 213.1 d with thedesigned second pressurizing medium chamber 200 a which is between thesecond actuating piston 205 on one side and the housing ring 213.1 inconnection with the additional piston 206.1 on the other side, which islocated in a part of the housing ring 213.1 containing the cylindricalrecess 213.1 a on the exterior.

The radial projection 213.1 cis formed in such a way on its side facingthe third actuating piston 206, that the latter, after the completion ofthe second partial piston travel b (FIG. 6 a), experiences there anend-of-travel limit. A corresponding limit of the first partial pistontravel a (cf. also FIG. 2) is done by the first individual adjustmentdevice 200.1 (FIG. 6) in that a modified drive sleeve 212* rests on anon-specified stop nut 214 (compare FIG. 2). The synchronization of themodified drive sleeve 212* is implemented, as is already seen from theembodiment of the individual adjustment device 200 according to FIGS. 1to 5 and as is also hereto described, through the second clamping flat205 a on the second actuating piston 205 working together with the thirdrecess 212 b on the modified drive sleeve 212*. The modified drivesleeve 212* via the second recess 212 a likewise engages on thenon-specified headpiece 203 a (compare also FIG. 4) in order to thusmove the first closing element 3, the independently actuated closingelement, in the course of the first partially open position T1 in one orthe other direction. The third actuating piston 206 engages using itsthird clamping flat 206 a on a non-specified first recess 204 a (comparealso FIG. 5) of the likewise non-specified third actuator stem 204, inorder to thus effect the execution of the second partially open positionT2 of the second closing element 4 in one or the other direction. Theaxial extension of the end of the modified drive sleeve 212* facing thethird actuating piston makes it necessary to provide the additionalpiston 206.1 with a coaxial piston bore 206.1 c, which surrounds themodified drive sleeve 212* with clearance on the outside.

Reference Numbers of the Abbreviations Used

-   1 valve housing-   1 a first valve housing member-   1 b second valve housing member-   2 seat ring-   2 a first seat surface-   2 b second seat surface-   2 c connection orifice-   3 first closing element-   3 a first control rod-   4 second closing element-   4 a second control rod-   5 leakage chamber-   6 lantern housing-   7 control device-   7 a position indicator rod-   7 b first pressurizing medium connection-   8 first seat seal (radial, axial)-   9 second seat seal (radial, axial)-   10 seal (axial)-   11 cleaning solution connection-   100 main adjustment device-   100 a first pressurizing medium chamber-   101/102 main adjustment device housing-   101 first housing member-   102 second housing member-   103 first actuator stem-   103 a pressurizing medium bore hole-   103 b cross holes-   103 c first stop face-   104 first actuating piston-   105 main spring-   200 individual adjustment device-   200.1 first individual adjustment device-   200.2 second individual adjustment device-   200 a second pressurizing medium chamber-   200 a* preceding second pressurizing medium chamber-   200 b third pressurizing medium chamber-   200 c fourth pressurizing medium chamber-   201/202 housing of the individual adjustment devices-   201 third housing member-   202 fourth housing member-   203 second actuator stem-   203 a headpiece-   203 b second stop face-   203 c first clamping flat-   204 third actuator stem-   204 a, first recess-   205 second actuating piston-   205 a second clamping flat-   206 third actuating piston-   206 a third clamping flat-   200 b first pressurizing medium channel-   206.1 additional piston-   206.1 a exterior piston section-   206.1 b interior piston section-   206.1 c coaxial piston bore-   206.1 d second pressurizing medium channel-   206.2 screwed connection-   207 second spring-   208 second pressurizing medium connection-   209 third pressurizing medium connection-   210 fourth pressurizing medium connection-   211 lock nut-   212 drive sleeve-   212* modified drive sleeve-   212 a second recess-   212 b third recess-   212 c third stop face-   213 stop ring-   213.1 housing ring-   213.1 a cylindrical cutout-   213.1 b coaxial through-bore-   213.1 c radial projection-   213.1 d connection channel-   214 stop nut-   214 a fourth stop face-   214 b cutout-   215 guide component-   215 a threaded portion-   215 b fifth stop face-   215 c sixth stop face-   216 first piston seal-   217 second piston seal-   218 seal-   a first partial piston travel-   b second partial piston travel-   c third partial piston travel-   d fourth partial piston travel-   D1 first pressurizing medium flow-   D2 second pressurizing medium flow-   D3 third pressurizing medium flow-   D_(a) outer diameter-   D_(i) inner diameter-   H full opening stroke (full open position)-   R cleaning solution-   R1 first seat cleaning stream-   R2 second seat cleaning stream-   T1 first partially open position (T1=a)-   T2 second partially open position (T2=b−c)

1. Device for actuating double seat valves with two closing elements (3,4) which are designed as seat discs and move independently to eachother, which enclose between them a leakage chamber (5), which isconnected via at least one path of travel with the surroundings of thedouble seat valve, with the independently actuated first closing element(3), that after a partial stroke comes to rest on the dependentlyactuated second closing element (4) and likewise transfers this with itsfurther opening movement into a full open position (H), with valve stems(3 a, 203, 103; 4 a, 204) which fit into one another in a telescopingmanner and that extend outward on the side of the second closing element(4) out of a valve housing (1), through which the closing elements (3,4), additionally to the full open position (H) and independent of eachother, are each able to be brought in a partially open position (TI,T2), whereby the full open position (H) is generated through a mainadjustment device (100) and the partially open positions (T1, T2)through the respective closing elements (3, 4) assigned individualadjustment devices (200; 200.1, 200.2), the individual adjustmentdevices (200; 200.1, 200.2) are designed stand-alone and are additivelyinserted between the main adjustment device (100) and the valve housing(1) and one actuating piston (205, 206 or 206/206.1) is respectivelyinstalled on a control rod (3 a, 203; 4 a, 204), which can be broughtaxially movable in one direction on the assigned control rod and in theopposite direction for engagement in a clamping connection with thiscontrol rod, and whereby the second partially open position (T2) of thesecond closing element (4) is limited by a permanent stop position ofthe third actuating piston (206; 206/206.1) which is provided in thehousing (201/202) of the individual adjustment device (200),characterized in that a stop position of the second actuating piston(205) is relative to the housing (201/202) provided for the firstpartially open position (T1) of the first closing element (3) and isadjustable from its exterior in the area between the main adjustmentdevice (100) and the individual adjustment devices (200) through a stopnut (214).
 2. Device according to claim 1, characterized in that thestop position of the second actuating piston (205) for the firstpartially open position (T1) is specified indirectly via a drive sleeve(212; 212*), which on the one side is lodged and sealed in the secondactuating piston (205) and on the other side on a guide component (215),that as a separate member engages from the outside in the third housingmember (201) and complementary supplements it, and whose axialdisplacement in the direction of the partially open position (T1) islimited by the stop nut (214), which is located on the guide component(215), is accessible from outside and is adjustable and fixable. 3.Device according to claim 2, characterized in that, the axial extensionof the drive sleeve (212; 212*) is designed larger than the full openposition (H).
 4. Device according to claim 1, characterized in that thethird actuating piston (206) on its side facing the second actuatingpiston (205) is connected tightly with a smaller diameter additionalpiston (206.1), but is able however to be loosened, that the additionalpiston (206.1) working together with a housing ring (213.1) fixed on thehousing (201/202) of the individual adjustment device (200) forms afourth pressurizing medium chamber (200 c), which is connected with athird pressurizing medium chamber (200 b) formed between the thirdactuating piston (206) and the fourth housing member (202), and thatwith the introduction of a third pressurizing medium flow (D3) to thethird pressurizing medium chamber (200 b) also an auxiliary forceaffecting the additional piston (206.1) results additionally in thefourth pressurizing medium chamber (200 c), which additivelysuperimposes on the force affecting the third actuating piston (206). 5.Device according to claim 4, characterized in that the additional piston(206.1) has a larger diameter exterior piston section (206.1 a) and asmaller diameter interior piston section (206.1 b), that the interiorpiston section (206.1 b) is sealed on its frontal end from the thirdactuating piston (206) and is screwed with this, that the exteriorpiston section (206.1 a) is sealed on its periphery from the shell of acylindrical cutout (213.1 a) in the housing ring (213.1) and theinterior piston section (206.1 b) is sealed on its periphery in acoaxial through bore (213.1 b) in the housing ring (213.1), and that inthe connection area of the third actuating piston (206) with theadditional piston (206.1) are located in the former a first pressurizingmedium channel (206 b) and in the latter a second pressurizing mediumchannel (206.1 d), which correspond with one another and connect thethird pressurizing medium chamber (200 b) and the fourth pressurizingmedium chamber (200 c) with one another permeable to the pressurizingmedium.
 6. Device according to claim 4, characterized in that thehousing ring (213.1) has a radial projection (213.1 c) on itscircumference, with which the housing ring (213.1) is positivelyfastened in the connection area between the third and the fourth housingmember (201, 202).
 7. Device according to claim 4, characterized in thata second pressurizing medium connection (208) for a second pressurizingmedium flow (D2) for pressurizing of the second actuating piston (205)located in the third housing member (201) discharges in a precedingsecond pressurizing medium chamber (200 a*) in the area between thethird actuating piston (206) and the housing ring (213.1), and that thepreceding second pressurizing medium chamber (200 a*) is connected witha second pressurizing medium chamber (200 a) formed between the secondactuating piston (205) on one side and the housing ring (213.1) inconnection with the additional piston (206.1) on the other side throughat least one connection channel (213.1 d), which is located in a part ofthe housing ring (213.1) containing the cylindrical cutout (213.1 a) onthe exterior.
 8. Device according to claim 1, characterized in that thestop position of the third actuating piston (206; 206/206.1) for thesecond partially open position (T2) is determined by a stop ring orhousing ring (213; 213.1), which is permanently located on a housing(201/202) and is axially moveable through the third actuating piston(206; 206/206.1).
 9. Device according to claim 1, characterized in thatthe first control rod (3 a) is screwed with its external threads with asecond actuator stem (203) in the area of a second individual adjustmentdevice (200.2), that the second actuator stem (203) is screwed with itsexternal threads likewise with a first actuator stem (103) of the mainadjustment device (100) in the area of a first individual adjustmentdevice (200.1), and that the screwed connection of the actuator stems(103, 203) are secured firmly by a lock nut (211) located on theexternal threads of the second actuator stem (203).
 10. Device accordingto claim 9, characterized in that the screwed connection of the firstcontrol rod (3 a) with the second actuator stem (203) is secured againstloosening by a threaded section, acting as a screw lock, located in theinternal threads of the second actuator stem (203).
 11. Device accordingto claim 9, characterized in that the first actuator stem (103) isprovided with a continuous pressurizing medium bore hole (103 a) in itslongitudinal axis, which leads over cross holes (103 b) into a firstpressurizing medium chamber (100 a) of the main adjustment device (100).12. Device according to claim 1, characterized in that the housingmembers (101, 102) of the main adjustment device (100) and each (201,202) of the individual adjustment devices (200) are made from housingrough parts of the same shape.
 13. Device according to claim 1,characterized in that the housing member (101, 102) of the mainadjustment device (100) and each (201, 202) of the individual adjustmentdevices (200) are each integrally joined with each other.
 14. Deviceaccording to claim 1, characterized in that the actuating pistons (205,206; 206/206.1) and an actuating piston (104) of the main adjustmentdevice (100) each are made out of corrosion resistant light alloy. 15.Device according to claim 1, characterized in that the followingarrangement, made up of a guide component (215) in connection with thestop nut (214), the drive sleeve (212), the second actuator stem (203)in connection with the lock nut (211), a third actuator stem (204) and asecond spring (207) located between the latter and the second actuatorstem (203), is totally extendable out of the assembled individualadjustment devices (200) in the direction of the main adjustment device(100) flanged on the latter.
 16. Device according to claim 1,characterized in that after loosening the screw connection between thefirst control rod (3 a) and the second actuator stem (203) thepretensioning of the second spring (207) is relieved.